EP3553324B1 - Soupape et système hydraulique équipé de celle-ci - Google Patents

Soupape et système hydraulique équipé de celle-ci Download PDF

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Publication number
EP3553324B1
EP3553324B1 EP19166519.9A EP19166519A EP3553324B1 EP 3553324 B1 EP3553324 B1 EP 3553324B1 EP 19166519 A EP19166519 A EP 19166519A EP 3553324 B1 EP3553324 B1 EP 3553324B1
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EP
European Patent Office
Prior art keywords
valve spool
main valve
counterbalance
working port
counterbalance valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP19166519.9A
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German (de)
English (en)
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EP3553324A1 (fr
Inventor
Zhongxiao Ma
Likui Zhai
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Danfoss Power Solutions Zhejiang Co Ltd
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Danfoss Power Solutions Zhejiang Co Ltd
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Publication of EP3553324A1 publication Critical patent/EP3553324A1/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/029—Counterbalance valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/10—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit
    • F16K11/20—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit operated by separate actuating members
    • F16K11/22—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit operated by separate actuating members with an actuating member for each valve, e.g. interconnected to form multiple-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F15B13/0403—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves a secondary valve member sliding within the main spool, e.g. for regeneration flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
    • F15B13/0418—Load sensing elements sliding within a hollow main valve spool
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
    • F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
    • F16K11/0708—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides comprising means to avoid jamming of the slide or means to modify the flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B2013/041—Valve members; Fluid interconnections therefor with two positions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B2013/0412—Valve members; Fluid interconnections therefor with three positions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50581—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5159—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6052—Load sensing circuits having valve means between output member and the load sensing circuit using check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6055—Load sensing circuits having valve means between output member and the load sensing circuit using pressure relief valves

Definitions

  • Embodiments of the present invention relate to a valve and a hydraulic system with the same.
  • a valve according to the preamble of claim 1 is known, for example, from WO 2007/090522 A1 , DE 26 49 775 A1 or DE 30 14 202 A1 .
  • a conventional counterbalance valve is disposed in a hydraulic system as a separate valve.
  • An object of embodiments of the present invention is to provide a valve in which a counterbalance valve is integrated.
  • the counterbalance valve is integrated in the valve.
  • Embodiments of the present invention further provide a hydraulic system comprising: the valve.
  • a valve 100 includes: a valve casing 1, a main valve spool 2 and a counterbalance valve spool 3.
  • the valve casing 1 includes: a valve casing body 1B, a main valve bore 1C extending in an axial direction in the valve casing body 1B; and a first working port (for example a port A) 30, a second working port (for example a port B) 34, a supply port (for example a port P) S and a return port (for example a port T) R formed in the valve casing body 1B (referring to FIG.4 ).
  • the main valve spool 2 is disposed in the main valve bore 1C of the valve casing 1 and is slidable in the main valve bore 1C to change the communication status between each of the first and second working ports 30 and 34 and each of the supply and return ports S and R, and the main valve spool 2 includes: a main valve spool body 2B, a main valve spool internal cavity 2C extending in the axial direction in the main valve spool body 2B; a main valve spool wall 2W surrounding the main valve spool internal cavity 2C; an inlet passage 17 which passes through the main valve spool wall 2W in a direction crossing the axial direction and which is configured for the second working port 34; and an outlet passage TP which passes through the main valve spool wall 2W in a direction crossing the axial direction and which has an inlet TP1 towards the main valve spool internal cavity 2C and an outlet TP2 towards the valve casing body 1B (referring to FIG.2 ).
  • the counterbalance valve spool 3 is disposed in the main valve spool internal cavity 2C of the main valve spool 2 and is slidable between a first counterbalance valve spool position (i.e. the position shown in FIGS. 1-16 ) and a second counterbalance valve spool position (i.e. the position shown in FIGS. 17-24 ).
  • the counterbalance valve spool 3 includes: a counterbalance valve spool body 3B; and a first counterbalance valve spool recess 23 formed on an outer periphery of the counterbalance valve spool body 3B.
  • a hydraulic fluid for example hydraulic oil
  • the counterbalance valve spool 3 and the main valve spool 2 constitute a counterbalance valve.
  • the valve 100 may be a load sensing valve or a load sensing multiple valve.
  • the first counterbalance valve spool recess 23 is configured to supply a fluid to the counterbalance valve.
  • the inlet passage 17 may extend in a radial direction of the main valve spool body 2B.
  • the main valve spool body 2B may have a substantially cylindrical shape.
  • a second working port inlet throttling groove 18 (as shown in FIG. 1 ) is in communication with the inlet passage 17.
  • the first counterbalance valve spool recess 23 may be an annular recess surrounding the outer periphery of the counterbalance valve spool body 3B, or a recess extending along a portion, in a peripheral or circumferential direction, of the outer periphery of the counterbalance valve spool body 3B.
  • a chamber is formed by the first counterbalance valve spool recess 23 and an inner wall of a second main spool internal cavity 2C2 of the main valve spool body 2B.
  • the outlet passage TP may extend substantially in the radial direction of the main valve spool body 2B.
  • the outlet passage TP may be a throttling passage.
  • the valve 100 may be a hydraulic control valve or the like.
  • the supply port S includes a first supply port 31 and a second supply port 33
  • the return port R includes a first return port 29 and a second return port 36 (referring to FIG. 4 ).
  • the main valve spool 2 is slidable among a first main valve spool position (i.e. the position shown in FIGS. 17-24 ), a middle main valve spool position (i.e. the position shown in FIGS. 1-8 ) and a second main valve spool position (i.e. the position shown in FIGS.
  • the second working port 34 is in communication with the second return port 36 through the inlet passage 17 configured for the second working port 34, the first counterbalance valve spool recess 23 and the outlet passage TP (referring to FIG. 19 ).
  • a hydraulic fluid for example the hydraulic oil
  • the second working port 34 enters the second return port 36 through the inlet passage 17 configured for the second working port 34, the first counterbalance valve spool recess 23 and the outlet passage TP by being throttled by the outlet passage TP.
  • the counterbalance valve spool 3 is in the first counterbalance valve spool position (i.e. the position shown in FIGS. 1-16 ), and the first working port 30 and the second working port 34 are disconnected from the first supply port 31 and the second supply port 33, respectively.
  • the counterbalance valve spool 3 is in the first counterbalance valve spool position (i.e. the position shown in FIGS. 1-16 )
  • the first working port 30 is in communication with the first return port 29, and the second working port 34 is in communication with the second supply port 33.
  • the first supply port 31 and the second supply port 33 may be in communication with each other, and the first return port 29 and the second return port 36 may be in communication with each other.
  • T denotes an oil tank
  • a and B denote the port A and the port B, respectively.
  • the first supply port 31, the second supply port 33, the first return port 29, the second return port 36, the first working port (for example the port A) 30, and the second working port (for example the port B) 34 may be formed by recesses formed on an inner wall of the main valve bore 1C of the valve casing body 1B. Each of the recesses may be formed on all or part of a circumference of the inner wall of the main valve bore 1C of the valve casing body 1B in a circumferential direction.
  • the main valve spool 2 is slidable among the first main valve spool position, the middle main valve spool position and the second main valve spool position to control the communications and the non-communications between the working ports and the supply and return ports S and R.
  • the main valve spool 2 may switch between two main valve spool positions or among four or more main valve spool positions to control communications and non-communications between working ports and supply and return ports S and R.
  • the outlet passage TP includes a plurality of sub-outlet passages 24, 28 and 35 (as shown in FIGS. 6 , 7 and 8 ) arranged in the axial direction, such that the greater a distance which the counterbalance valve spool 3 slides in a direction from the first counterbalance valve spool position towards the second counterbalance valve spool position is, the more sub-outlet passages 24, 28 and 35 are opened, and thus the greater a total flow area of these opened sub-outlet passages is (Referring to FIGS. 18-20 and 22-24 ).
  • the second working port 34 is in communication with the first counterbalance valve spool recess 23 through the inlet passage 17 configured for the second working port 34.
  • the sub-outlet passages 24, 28 and 35 may be two, three or more sub-outlet passages.
  • the outlet passage TP may be one outlet passage TP, or two or more outlet passages TP in substantially the same axial position, and each of the sub-outlet passages 24, 28 and 35 may be one sub-outlet passage, or two or more sub-outlet passages in substantially the same axial position.
  • the inlet passage 17 configured for the second working port 34 may be one inlet passage 17, or two or more inlet passages 17 in substantially the same axial position.
  • the sub-outlet passages 24, 28 and 35 may be sub-throttling passages.
  • the main valve spool internal cavity 2C of the main valve spool 2 includes: first and second main valve spool internal cavities 2C1 and 2C2 extending in the axial direction in the main valve spool body 2B; a main valve spool internal cavity partition wall 2P between the first and second main valve spool internal cavities 2C1 and 2C2; a main valve spool internal cavity partition wall through hole 9 formed in the main valve spool internal cavity partition wall 2P and communicating the first main valve spool internal cavity 2C1 with the second main valve spool internal cavity 2C2; and a counterbalance valve spring cavity 20 extending from the second main valve spool internal cavity 2C2 in a direction away from the first main valve spool internal cavity 2C1.
  • the counterbalance valve spool 3 is disposed in the second main valve spool internal cavity 2C2 of the main valve spool 2, and has a first end 3E1 adjacent to the main valve spool internal cavity partition wall 2P of the main valve spool 2, and a second end 3E2 opposite to the first end 3E1.
  • the valve 100 further includes: a counterbalance valve spring seat 4 disposed in the counterbalance valve spring cavity 20 of the main valve spool 2 and having an end 4E facing towards the counterbalance valve spool 3; and counterbalance valve springs 5 and 6 disposed in the counterbalance valve spring cavity 20 of the main valve spool 2 and configured to apply a force to the counterbalance valve spring seat 4 to bias the counterbalance valve spring seat 4 towards the counterbalance valve spool 3, so that the end 4E of the counterbalance valve spring seat 4 abuts against the second end 3E2 of the counterbalance valve spool 3 and applies a pushing force to the counterbalance valve spool 3 in a direction from the second counterbalance valve spool position towards the first counterbalance valve spool position.
  • the main valve spool internal cavity partition wall through hole 9 may be a damping hole, or any other appropriate through hole.
  • the main valve spool internal cavity partition wall through hole 9 may extend substantially in the axial direction.
  • the two counterbalance valve springs 5 and 6 are shown in the figures, a single counterbalance valve spring may be used.
  • An opening pressure of the counterbalance valve is determined by the counterbalance valve springs 5 and 6.
  • the damping hole may be configured to reduce an impact pressure when the counterbalance valve is opened.
  • the first end 3E1 may have a shape of a truncated cone.
  • the main valve spool 2 further includes a first working port pressure acquisition hole 21 (as shown in FIG. 18 ) which passes through the main valve spool wall 2W of the main valve spool 2 in a direction crossing the axial direction.
  • the first working port pressure acquisition hole 21 communicates the first working port 30 with the first main valve spool internal cavity 2C1 of the main valve spool 2.
  • the first working port pressure acquisition hole 21 is configured to acquire a pressure value of the first working port 30 in operation.
  • the first working port pressure acquisition hole 21 may extend substantially in the radial direction of the main valve spool body 2B.
  • the main valve spool 2 further includes a second working port pressure acquisition hole (for example a load sensing (LS) pressure acquisition hole for the port B) 8 (as shown in FIG. 17 ) which passes through the main valve spool wall 2W of the main valve spool 2 in a direction crossing the axial direction.
  • LS load sensing
  • the second working port pressure acquisition hole 8 communicates the counterbalance valve spring cavity 20 with the second return port 36.
  • the second working port pressure acquisition hole 8 is configured to acquire a size of a pressure value of the second working port 34 in operation.
  • the second working port pressure acquisition hole 8 may extend obliquely to the axial direction.
  • the counterbalance valve spring seat 4 includes: a head 4H having the end 4E facing towards the counterbalance valve spool 3; and a rod 4S inserted into the counterbalance valve springs, and the main valve spool 2 further includes a plug 7 which closes an end of the main valve spool internal cavity 2C of the main valve spool 2, and which is configured to restrict, by an abutment against the rod 4S of the counterbalance valve spring seat 4, a distance which the counterbalance valve spring scat 4 slides, and thus a distance which the counterbalance valve spool 3 slides in a direction from the first counterbalance valve spool position towards the second counterbalance valve spool position.
  • the counterbalance valve spring cavity 20 of the main valve spool 2 has a greater cross-sectional size than the second main spool internal cavity 2C2.
  • the counterbalance valve spool 3 is in the second counterbalance valve spool position so that the second end 3E2 of the counterbalance valve spool 3 enters the counterbalance valve spring cavity 20, and the counterbalance valve spring cavity 20 is in communication with the second return port 36 through a gap between the counterbalance valve spring seat 4 and the inner wall of the counterbalance valve spring cavity 20 of the main valve spool 2, a gap between the counterbalance valve spool 3 and the inner wall of the counterbalance valve spring cavity 20 of the main valve spool 2, and the second working port pressure acquisition hole 8.
  • the counterbalance valve spring seat 4 further includes: a counterbalance valve spring seat recess 25 (as shown in FIGS. 17 and 18 ) formed at an end surface of the end 4E on an outer periphery of the end 4E.
  • the counterbalance valve spring cavity 20 is in communication with the second return port 36 through the gap between the counterbalance valve spring seat 4 and the inner wall of the counterbalance valve spring cavity 20 of the main valve spool 2, the gap between the counterbalance valve spool 3 and the inner wall of the counterbalance valve spring cavity 20 of the main valve spool 2, the counterbalance valve spring seat recess 25, and the second working port pressure acquisition hole 8.
  • each of the first main valve spool internal cavity 2C1, the second main valve spool internal cavity 2C2 and the counterbalance valve spring cavity 20 may have a circular cross section.
  • the counterbalance valve spring seat recess 25 may be an annular recess surrounding the outer periphery of the counterbalance valve spring seat 4, or a recess extending along a portion, in a peripheral or circumferential direction, of the outer periphery of the counterbalance valve spring seat 4.
  • a chamber is formed by the counterbalance valve spring seat recess 25 and the inner wall of the counterbalance valve spring cavity 20.
  • a diameter of the second end 3E2 of the counterbalance valve spool 3 may be less than or equal to a diameter of a bottom of the counterbalance valve spring seat recess 25.
  • the valve casing 1 further includes a working port pressure detection cavity 32 (as shown in FIG. 17 and 20 ) formed in the valve casing body 1B, and the main valve spool 2 further includes a first working port pressure feedback hole 26 (as shown in FIG. 19 ) which passes through the main valve spool wall 2W of the main valve spool 2 in a direction crossing the axial direction.
  • the first working port pressure feedback hole 26 communicates the first main valve spool internal cavity 2C1 with the working port pressure detection cavity 32 so that the working port pressure detection cavity 32 is in communication with the first working port 30 through the first working port pressure feedback hole 26, the first main valve spool internal cavity 2C1 and the first working port pressure acquisition hole 21 (as shown in FIG. 18 ).
  • the first working port pressure feedback hole 26 may be configured to feed back a pressure acquired by the first working port pressure acquisition hole 21 to the working port pressure detection cavity 32.
  • the working port pressure detection cavity (for example an LS chamber) 32 is configured to feed back the pressure to a pump.
  • the first working port pressure feedback hole 26 may extend substantially in the radial direction of the main valve spool body 2B.
  • the working port pressure detection cavity 32 may be formed by a recess formed on the inner wall of the main valve bore 1C of the valve casing body 1B.
  • the recess may be formed on all or part of the circumference of the inner wall of the main valve bore 1C of the valve casing body 1B in the circumferential direction.
  • the valve 100 further includes a connection hole extending in the axial direction in an end of the main valve spool body 2B, for example a connection hole extending from the first main valve spool internal cavity 2C1 in a direction away from the second main valve spool internal cavity 2C2.
  • the valve 100 further includes a biasing assembly configured to apply a force to the main valve spool 2 so as to bias the main valve spool 2 towards the middle main valve spool position.
  • the biasing assembly includes a supporting shaft 13 (for example a hook) (such as shown in FIGS. 1 and 17 ).
  • the biasing assembly further includes: a first main valve spool spring seat and a second main valve spool spring seat.
  • Each of the first main valve spool spring seat and the second main valve spool spring seat includes a sleeve, and a flange disposed at an end of the sleeve.
  • the biasing assembly further includes a main valve spool spring 11.
  • the first main valve spool spring seat and the second main valve spool spring seat are fitted over the supporting shaft 13 to be slidable with respect to the supporting shaft 13.
  • the sleeves of the first main valve spool spring seat and the second main valve spool spring seat are inserted into the main valve spool spring 11 from two ends of the main valve spool spring 11, respectively, such that the flanges of the first main valve spool spring seat and the second main valve spool spring seat abut against the two ends of the main valve spool spring 11, respectively.
  • the other end of the supporting shaft 13 has a shoulder.
  • An inner diameter of each of the flanges of the first main valve spool spring seat and the second main valve spool spring seat is less than an outer diameter of the main valve spool body 2B, and an outer diameter of each of the flanges of the first main valve spool spring scat and the second main valve spool spring scat is greater than a diameter of the main valve bore 1C of the valve casing body 1B of the valve casing 1.
  • the main valve spool 2 further includes: a first working port return throttling groove 14 formed in the main valve spool body 2B and configured to control a magnitude of a flow rate of a fluid flowing from the first working port 30 to the first return port 29; an inlet passage 17 configured for the second working port 34 and serving as an inlet of the counterbalance valve; a second working port inlet throttling groove 18 configured to control a magnitude of a flow rate of a fluid flowing from the second supply port 33 to the second working port 34; and a first working port inlet throttling groove 19 configured to control a magnitude of a flow rate of a fluid flowing from the first supply port 31 to the first working port 30.
  • An annular groove is formed on an outer periphery of the main valve spool body 2B, the first working port return throttling groove 14 is in communication with the annular groove on one side of the annular groove, and the first working port inlet throttling groove 19 is in communication with the annular groove on the other side of the annular groove.
  • the first main valve spool internal cavity 2C1 and the counterbalance valve spring cavity 20 are in communication with the first return port 29 and the second return port 36, respectively.
  • the first working port pressure acquisition hole 21 communicates the first return port 29 with the first main valve spool internal cavity 2C1 of the main valve spool 2.
  • the second working port pressure acquisition hole 8 communicates the counterbalance valve spring cavity 20 with the second return port 36.
  • the counterbalance valve spring cavity 20 is in communication with the second return port 36 through the gap between the counterbalance valve spring seat 4 and the inner wall of the counterbalance valve spring cavity 20 of the main valve spool 2, and the second working port pressure acquisition hole 8.
  • the counterbalance valve spring cavity 20 is in communication with the second return port 36 through the gap between the counterbalance valve spring seat 4 and the inner wall of the counterbalance valve spring cavity 20 of the main valve spool 2, the counterbalance valve spring seat recess 25, and the second working port pressure acquisition hole 8.
  • the first working port pressure feedback hole 26 communicates the first main valve spool internal cavity 2C1 with the working port pressure detection cavity 32, and the first working port pressure acquisition hole 21 is in communication with the first return port 29, so that the working port pressure detection cavity 32 is in communication with the first return port 29 through the first working port pressure feedback hole 26, the first main valve spool internal cavity 2C1 and the first working port pressure acquisition hole 21.
  • the main valve spool 2 further includes a second working port pressure feedback hole 27 which passes through the main valve spool wall 2W of the main valve spool 2 in a direction crossing the axial direction.
  • the counterbalance valve spool 3 further includes: a counterbalance valve spool axial hole 15 which is formed in the counterbalance valve spool body 3B substantially in the axial direction; and a counterbalance valve spool communication hole 15C which is formed in the counterbalance valve spool body 3B in a direction crossing the axial direction and which is in communication with the counterbalance valve spool axial hole 15.
  • the counterbalance valve spool communication hole 15C may be in communication with the second working port pressure feedback hole 27 through a second counterbalance valve spool recess 22 formed on the outer periphery of the counterbalance valve spool body 3B.
  • the counterbalance valve spring scat 4 further includes: a counterbalance valve spring seat groove 16 (as shown in FIG.1 ) formed at an end surface of the end 4E and extending in a direction crossing the axial direction.
  • the second working port pressure feedback hole 27 communicates the counterbalance valve spool axial hole 15 with the working port pressure detection cavity 32 through the counterbalance valve spool communication hole 15C
  • the second working port pressure acquisition hole 8 communicates the counterbalance valve spool axial hole 15 with the second return port 36 through the counterbalance valve spring seat groove 16, so that the working port pressure detection cavity 32 is in communication with the second return port 36 through the second working port pressure feedback hole 27, the counterbalance valve spool communication hole 15C, the counterbalance valve spool axial hole 15, the counterbalance valve spring seat groove 16 and the second working port pressure acquisition hole 8, as shown in FIGS.
  • the second working port pressure feedback hole 27 may be configured to feed back a pressure acquired by the second working port pressure acquisition hole 8 to the working port pressure detection cavity 32.
  • the counterbalance valve spring seat groove 16 may extend on the end surface of the end 4E such that an end of the counterbalance valve spring seat groove 16 extends to an edge of the end surface of the end 4E, so that the counterbalance valve spring seat groove 16 is in communication with the counterbalance valve spring scat recess 25.
  • the counterbalance valve spring scat groove 16 is in communication with the counterbalance valve spool axial hole 15.
  • the end 4E of the counterbalance valve spring seat 4 abuts against the second end 3E2 of the counterbalance valve spool 3.
  • a sealing contact may be formed between the end surface of the end 4E of the counterbalance valve spring seat 4 and an end surface of the second end 3E2 of the counterbalance valve spool 3.
  • the second working port pressure feedback hole 27 may extend substantially in the radial direction of the main valve spool body 2B, as shown in FIG. 3 .
  • the counterbalance valve spring seat groove 16 communicates the counterbalance valve spool axial hole 15 with the counterbalance valve spring seat recess 25 formed in the outer periphery of the end 4E of the counterbalance valve spring seat 4. As shown in FIGS. 1-8 , according to an embodiment of the present invention, the counterbalance valve spring seat groove 16 communicates the counterbalance valve spool axial hole 15 with the counterbalance valve spring seat recess 25 formed in the outer periphery of the end 4E of the counterbalance valve spring seat 4. As shown in FIGS.
  • the second working port pressure feedback hole 27 communicates the counterbalance valve spool axial hole 15 with the working port pressure detection cavity 32 through the counterbalance valve spool communication hole 15C
  • the second working port pressure acquisition hole 8 communicates the counterbalance valve spool axial hole 15 with the second return port 36 through the counterbalance valve spring seat recess 25 and the counterbalance valve spring seat groove 16, so that the working port pressure detection cavity 32 is in communication with the second return port 36 through the second working port pressure feedback hole 27, the counterbalance valve spool communication hole 15C, the counterbalance valve spool axial hole 15, the counterbalance valve spring seat groove 16, the counterbalance valve spring seat recess 25 and the second working port pressure acquisition hole 8.
  • the counterbalance valve spring seat recess 25 may be configured to feed back a load sensing (LS) pressure.
  • the counterbalance valve spool 3 further includes: the second counterbalance valve spool recess 22 formed on the outer periphery of the counterbalance valve spool body 3B.
  • the counterbalance valve spool communication hole 15C communicates the second counterbalance valve spool recess 22 with the counterbalance valve spool axial hole 15.
  • the second working port pressure feedback hole 27 is in communication with the counterbalance valve spool communication hole 15C through the second counterbalance valve spool recess 22.
  • the second counterbalance valve spool recess 22 may be configured to feed back a load sensing (LS) pressure.
  • the second counterbalance valve spool recess 22 may be an annular recess surrounding the outer periphery of the counterbalance valve spool body 3B, or a recess extending along a portion, in the peripheral or circumferential direction, of the outer periphery of the counterbalance valve spool body 3B.
  • a chamber is formed by the second counterbalance valve spool recess 22 and the inner wall of the second main spool internal cavity 2C2 of the main valve spool body 2B.
  • An outer peripheral surface of the counterbalance valve spool body 3B is in sealing contact with a surface of the inner wall of the second main spool internal cavity 2C2.
  • the first main valve spool internal cavity 2C1 is in communication with the first return port 29.
  • the first working port pressure acquisition hole 21 communicates the first return port 29 with the first main valve spool internal cavity 2C1 of the main valve spool 2.
  • the second working port pressure acquisition hole 8 communicates the counterbalance valve spring cavity 20 with the second working port 34.
  • the counterbalance valve spring cavity 20 is in communication with the second working port 34 through the gap between the counterbalance valve spring seat 4 and the inner wall of the counterbalance valve spring cavity 20 of the main valve spool 2, and the second working port pressure acquisition hole 8.
  • FIGS. 9-16 especially as shown in FIG.
  • the counterbalance valve spring cavity 20 is in communication with the second working port 34 through the gap between the counterbalance valve spring seat 4 and the inner wall of the counterbalance valve spring cavity 20 of the main valve spool 2, the counterbalance valve spring seat recess 25, and the second working port pressure acquisition hole 8.
  • the second working port pressure feedback hole 27 communicates the counterbalance valve spool axial hole 15 with the working port pressure detection cavity 32 through the counterbalance valve spool communication hole 15C, and as shown in FIG.
  • the second working port pressure acquisition hole 8 communicates the counterbalance valve spool axial hole 15 with the second working port 34 through the counterbalance valve spring seat groove 16, so that the working port pressure detection cavity 32 is in communication with the second working port 34 through the second working port pressure feedback hole 27, the counterbalance valve spool communication hole 15C, the counterbalance valve spool axial hole 15, the counterbalance valve spring seat groove 16 and the second working port pressure acquisition hole 8.
  • the second working port pressure feedback hole 27 communicates the counterbalance valve spool axial hole 15 with the working port pressure detection cavity 32 through the counterbalance valve spool communication hole 15C, and as shown in FIG.
  • the second working port pressure acquisition hole 8 communicates the counterbalance valve spool axial hole 15 with the second working port 34 through the counterbalance valve spring seat recess 25 and the counterbalance valve spring seat groove 16, so that the working port pressure detection cavity 32 is in communication with the second working port 34 through the second working port pressure feedback hole 27, the counterbalance valve spool communication hole 15C, the counterbalance valve spool axial hole 15, the counterbalance valve spring seat groove 16, the counterbalance valve spring seat recess 25 and the second working port pressure acquisition hole 8.
  • the second working port pressure feedback hole 27 may be in communication with the counterbalance valve spool communication hole 15C through the second counterbalance valve spool recess 22.
  • Embodiments of the present invention further provide a hydraulic system 200 including the valve 100.
  • the hydraulic system 200 further includes: a hydraulic cylinder 41 which has chambers located on both sides of a piston of the hydraulic cylinder 41 and respectively connected with the first working port 30 and the second working port 34 (it can be understood that herein the hydraulic cylinder is merely an example of an actuator and any other actuator such as a motor may be used in the hydraulic system); a first working port overflow valve 42 connected with the first working port 30; a second working port overflow valve 40 connected with the second working port 34; a pump 37, such as a load sensing variable displacement pump, connected with the first supply port 31 and the second supply port 33 through a check valve 44; a shuttle valve 38 through which the working port pressure detection cavity 32 feeds back the pressure to a feedback port of the pump 37; and a pressure detection overflow valve (load sensing (LS) overflow valve) 39 connected with the feedback port of the pump 37.
  • a hydraulic cylinder 41 which has chambers located on both sides of a piston
  • valve 100 An operational principle of the valve 100 and an operational principle of the hydraulic system 200 in the state where the main valve spool 2 is in the middle main valve spool position is described as below with reference to FIGS. 1-8 .
  • valve 100 The operational principle of the valve 100 and the operational principle of the hydraulic system 200 in the state where the main valve spool 2 is in the second main valve spool position is described as below with reference to FIGS. 9-16 .
  • the fluid flows from the second supply port 33 to the second working port 34 (port B).
  • a magnitude of a flow rate of the fluid is adjustable by the second working port inlet throttling groove 18, and a direction of motion D of the piston of the hydraulic cylinder 41 is as shown in FIGS. 13-16 .
  • the second working port pressure acquisition hole 8 is in communication with the second working port 34 as shown in FIG.
  • the first main valve spool internal cavity 2C1 is in communication with the first return port 29 through the first working port pressure acquisition hole 21 so that a pressure of the first main valve spool internal cavity 2C1 is released.
  • the operating state of the counterbalance valve is as follows.
  • valve 100 The operational principle of the valve 100 and the operational principle of the hydraulic system 200 in the state where the main valve spool 2 is in the first main valve spool position is described as below with rcfcrcncc to FIGS. 17-24 .
  • the hydraulic fluid flows from the first supply port 31 to the first working port 30 (port A), as shown in FIG. 17 .
  • a magnitude of a flow rate of the hydraulic fluid is adjustable by the first working port inlet throttling groove 19, and the direction of motion D of the piston of the hydraulic cylinder 41 is as shown in FIGS. 21-24 .
  • a pressure of the first working port 30 is fed back to the working port pressure detection cavity 32 through the first working port pressure acquisition hole 21, the first main valve spool internal cavity 2C1, and the first working port pressure feedback hole 26, thereby achieving the load sensing control.
  • the second working port pressure feedback hole 27 is disconnected from the working port pressure detection cavity 32, as shown in FIG. 19 .
  • the operating state of the counterbalance valve is as follows.
  • a counterbalance valve is integrated in a spool of a load sensing multiple valve.
  • a function of the counterbalance valve is achieved.
  • a load sensing (LS) pressure is fed back to the working port pressure detection cavity 32 through the fit clearance between the counterbalance valve spring seat 4 and the inner wall of the counterbalance valve spring cavity 20 of the main valve spool 2, and the fit clearance between the counterbalance valve spool 3 and the inner wall of the counterbalance valve spring cavity 20 of the main valve spool 2, thereby achieving both a load sensing function and the function of the counterbalance valve.
  • an integrity level is greatly improved.
  • a required controlling pressure is successfully achieved in a narrow space by the two springs and the first end 3E1 of the counterbalance valve spool 3 having a shape of a truncated cone.
  • valve according to the embodiments of the present invention may be applied to cranes, forklifts, and the like.
  • the counterbalance valve is configured to control actions of a negative load of a hydraulic cylinder or a motor, such as lowering the negative load and forward tilting the negative load, so that a velocity of movement of the hydraulic cylinder or the motor is controllable, and a stable movement is achieved.
  • the counterbalance valve is disposed in the main valve spool.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
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  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Safety Valves (AREA)
  • Multiple-Way Valves (AREA)

Claims (15)

  1. Soupape (100), comprenant
    un carter de soupape (1) comprenant : un corps de carter de soupape (1B), un alésage de soupape principal (1C) s'étendant dans une direction axiale dans le corps de carter de soupape (1B) ; et un premier port de travail (30), un second port de travail (34), un port d'alimentation (S) comprenant un premier port d'alimentation (31) et un second port d'alimentation (33) et un port de retour (R) comprenant un premier port de retour (29) et un second port de retour (36) formés dans le corps de carter de soupape (1B) ;
    une bobine de soupape principale (2) qui est disposée dans l'alésage de soupape principal (1C) du carter de soupape (1B) et qui peut coulisser dans l'alésage de soupape principal (1C) pour changer l'état de communication entre chacun des premier et second ports de travail (30, 34) et chacun des ports d'alimentation et de retour (S, R), la bobine de soupape principale (2) pouvant coulisser parmi une première position de bobine de soupape principale, une position médiane de bobine de soupape principale et une seconde position de bobine de soupape principale pour commander l'état de communication entre le premier port de travail (30) et chacun du premier port d'alimentation (31) et du premier port de retour (33), et l'état de communication entre le second port de travail (34) et chacun du second port d'alimentation (33) et du second port de retour (36), la bobine de soupape principale (2) comprenant :
    un corps de bobine de soupape principale (2B), une cavité interne de bobine de soupape principale (2C) s'étendant dans la direction axiale dans le corps de bobine de soupape principal (2B) ;
    une paroi de bobine de soupape principale (2W) entourant la cavité interne de bobine de soupape principale (2C) ;
    un passage d'entrée (17) qui passe à travers la paroi de bobine de soupape principale (2W) dans une direction croisant la direction axiale et qui est configuré pour le second port de travail (34) ; et
    un passage de sortie (TP) qui passe à travers la paroi de bobine de soupape principale (2W) dans une direction croisant la direction axiale, et qui a une entrée (TP1) en direction de la cavité interne de bobine de soupape principale (2C) et une sortie (TP2) en direction du corps de carter de soupape (1B) ; et
    une bobine de soupape de contrebalance (3) qui est disposée dans la cavité interne de bobine de soupape principale (2C) de la bobine de soupape principale (2) et qui peut coulisser par rapport à la bobine de soupape principale (2) entre une première position de bobine de soupape de contrebalance et une seconde position de bobine de soupape de contrebalance, la bobine de soupape de contrebalance (3) comprenant :
    un corps de bobine de soupape de contrebalance (3B) ; et
    un premier creux de bobine de soupape de contrebalance (23) formé sur une périphérie extérieure du corps de bobine de soupape de contrebalance (3B),
    dans laquelle dans un état où la bobine de soupape de contrebalance (3) est dans la première position de bobine de soupape de contrebalance, l'entrée (TP1) du passage de sortie (TP) de la bobine de soupape principale (3) est fermée par la bobine de soupape de contrebalance (3) ; et
    dans un état où la bobine de soupape de contrebalance (3) est dans la seconde position de bobine de soupape de contrebalance, l'entrée (TP1) du passage de sortie (TP) de la bobine de soupape principale (2) est ouverte par la bobine de soupape de contrebalance (3) par le premier creux de bobine de soupape de contrebalance (23) de la bobine de soupape de contrebalance (3), de façon à ce que le second port de travail (34) soit en communication avec le port de retour (R) à travers le passage d'entrée (17) configuré pour le second port de travail (34), le premier creux de bobine de soupape de contrebalance (23) et le passage de sortie (TP), dans laquelle dans un état où la bobine de soupape principale est (2) dans la première position de bobine de soupape principale, le premier port de travail (30) est en communication avec le premier port d'alimentation (31), la bobine de soupape de contrebalance (3) est dans la seconde position de bobine de soupape de contrebalance et le second port de travail (34) est en communication avec le second port de retour (36) à travers le passage d'entrée (17) configuré pour le second port de travail (34), le premier creux de bobine de soupape de contrebalance (23) et le passage de sortie (TP) ;
    dans un état où la bobine de soupape principale (2) est dans la position médiane de bobine de soupape principale, la bobine de soupape de contrebalance (3) est dans la première position de bobine de soupape de contrebalance, et le premier port de travail (30) et le second port de travail (34) sont déconnectés du premier port d'alimentation (31) et du second port d'alimentation (33) respectivement ; et
    dans un état où la bobine de soupape principale (2) est dans la seconde position de bobine de soupape principale, la bobine de soupape de contrebalance (3) est dans la première position de bobine de soupape de contrebalance, le premier port de travail (30) est en communication avec le premier port de retour (29), et le second port de travail (34) est en communication avec le second port d'alimentation (33),
    et caractérisée en ce que
    le carter de soupape (1) comprend en outre une cavité de détection de pression de port de travail (32) formée dans le corps de carter de soupape (1B) et ouvrant vers l'alésage de soupape principale (1C), et un premier passage de retour et un second passage de retour sont formés dans la bobine de soupape principale (2), dans laquelle :
    lorsque la bobine de soupape principale (2) est dans la position médiane de bobine de soupape principale, chacun des premier passage de retour et second passage de retour fait communiquer la cavité de détection de pression de port de travail (32) avec le port de retour (R) ;
    lorsque la bobine de soupape principale (2) est dans la première position de bobine de soupape principale, le premier passage de retour fait communiquer la cavité de détection de pression de port de travail (32) avec le premier port de travail (30) et le second passage de retour est déconnecté de la cavité de détection de pression de port de travail (32) ;
    lorsque la bobine de soupape principale (2) est dans la seconde position de bobine de soupape principale, le second passage de retour fait communiquer la cavité de détection de pression de port de travail (32) avec le second port de travail (34) et le premier passage de retour est déconnecté de la cavité de détection de pression de port de travail (32).
  2. Soupape selon la revendication 1, dans laquelle :
    le passage de sortie comprend une pluralité de sous-passages de sortie agencés dans la direction axiale de telle façon que plus la distance sur laquelle la bobine de soupape de contrebalance glisse est grande dans une direction allant de la première position de bobine de soupape de contrebalance vers la seconde position de bobine de soupape de contrebalance, plus il y a de sous-passages de sortie ouverts.
  3. Soupape selon la revendication 1, dans laquelle :
    la cavité interne de bobine de soupape principale (2C) de la bobine de soupape principale (2) comprend : des première et seconde cavités internes de bobine de soupape principale (2C1, 2C2) s'étendant dans la direction axiale dans le corps de bobine de soupape principal (2B) ; une cloison de séparation de cavité interne de bobine de soupape principale (2P) entre les première et seconde cavités internes de bobine de soupape principale (2C1, 2C2) ; un trou traversant de cloison de séparation de cavité interne de bobine de soupape principale (9) formé dans la cloison de séparation de cavité interne de bobine de soupape principale (2P) et faisant communiquer la première cavité interne de bobine de soupape principale (2C1) avec la seconde cavité interne de bobine de soupape principale (2C2) ; et une cavité de ressort de soupape de contrebalance (20) s'étendant de la seconde cavité interne de bobine de soupape principale (2C2) dans une direction à distance de la première cavité interne de bobine de soupape principale (2C1) ;
    la bobine de soupape de contrebalance (3) est disposée dans la seconde cavité interne de bobine de soupape principale (2C2) de la bobine de soupape principale (2), et a une première extrémité (3E1) adjacente à la cloison de séparation de cavité interne de bobine de soupape principale (2P) de la bobine de soupape principale (2), et une seconde extrémité (3E2) opposée à la première extrémité (3E1) ;
    la soupape (1) comprend en outre :
    un siège de ressort de soupape de contrebalance (4) disposé dans la cavité de ressort de soupape de contrebalance (20) de la bobine de soupape principale (2) et ayant une extrémité (4E) orientée vers la bobine de soupape de contrebalance (3) ; et
    un ressort de soupape de contrebalance (5, 6) disposé dans la cavité de ressort de soupape de contrebalance (20) de la bobine de soupape principale (2) et configuré pour appliquer une force au siège de ressort de soupape de contrebalance (4) pour décaler le siège de ressort de soupape de contrebalance (4) vers la bobine de soupape de contrebalance (3) de façon à ce que l'extrémité du siège de ressort de soupape de contrebalance (4) soit adjacente à la seconde extrémité (3E2) de la bobine de soupape de contrebalance et applique une force de poussée à la bobine de soupape de contrebalance (3) dans une direction allant de la seconde position de bobine de soupape de contrebalance vers la première position de bobine de soupape de contrebalance.
  4. Soupape selon la revendication 3, dans laquelle :
    le siège de ressort de soupape de contrebalance (4) comprend : une tête (4H) ayant l'extrémité orientée vers la bobine de soupape de contrebalance (3) ; et une tige (4S) insérée dans le ressort de soupape de contrebalance (5, 6), et
    la bobine de soupape principale (2) comprend en outre un bouchon (7) qui ferme une extrémité de la cavité interne de bobine de soupape principale (2C) de la bobine de soupape principale (2), et qui est configuré pour restreindre, par une butée contre la tige (4S) du siège de ressort de soupape de contrebalance (4), une distance sur laquelle le siège de ressort de soupape de contrebalance (4) glisse, et ainsi une distance sur laquelle la bobine de soupape de contrebalance (3) glisse dans une direction allant de la première position de bobine de soupape de contrebalance vers la seconde position de bobine de soupape de contrebalance.
  5. Soupape selon la revendication 3, dans laquelle :
    le premier passage de retour comprend un premier trou d'acquisition de pression de port de travail (21) qui passe à travers la paroi de bobine de soupape principale (2W) de la bobine de soupape principale (2) dans une direction croisant la direction axiale et qui ouvre vers la première cavité interne de bobine de soupape principale (2C1), dans un état où la bobine de soupape principale (2) dans l'alésage de soupape principal (1C) est dans la première position de bobine de soupape principale, le premier trou d'acquisition de pression de port de travail (21) est en communication avec le premier port de travail (30) de façon à ce que le premier port de travail (30) soit en communication avec la première cavité interne de bobine de soupape principale (2C1) de la bobine de soupape principale (2) par le premier trou d'acquisition de pression de port de travail (21).
  6. Soupape selon la revendication 5, dans laquelle :
    le premier passage de retour comprend un premier trou de retour de pression de port de travail (26) qui passe à travers la paroi de bobine de soupape principale (2W) de la bobine de soupape principale (2) dans une direction croisant la direction axiale et qui ouvre vers la première cavité interne de bobine de soupape principale (2C1), dans l'état où la bobine de soupape principale (2) dans l'alésage de soupape principal est dans la première position de bobine de soupape principale, le premier trou de retour de pression de port de travail (26) est en communication avec la cavité de détection de pression de port de travail (32) de façon à ce que la cavité de détection de pression de port de travail (32) soit en communication avec le premier port de travail par le premier trou de retour de pression (26) de port de travail (30), la première cavité interne de bobine de soupape principale (2C1) et le premier trou d'acquisition de pression de port de travail (21).
  7. Soupape selon la revendication 5, dans laquelle :
    le trou traversant de cloison de séparation de cavité interne de bobine de soupape principale (9) est un trou d'amortissement, dans l'état où la bobine de soupape principale (2) dans l'alésage de soupape principal (1C) est dans la première position de bobine de soupape principale, une force d'ouverture appliquée à la bobine de soupape de contrebalance (3) à travers le trou d'amortissement par une pression dans la première cavité interne de bobine de soupape principale (2C1) est supérieure à une force appliquée à la bobine de soupape de contrebalance (3) par le ressort de soupape de contrebalance (5, 6), de telle façon que la bobine de soupape de contrebalance (3) est forcée de se déplacer de la première position de bobine de soupape de contrebalance vers la seconde position de bobine de soupape de contrebalance.
  8. Soupape selon la revendication 6, dans laquelle :
    dans l'état où la bobine de soupape principale (2) dans l'alésage de soupape principal (1C) est dans la position médiane de bobine de soupape principale, le premier trou de retour de pression de port de travail (26) est en communication avec la cavité de détection de pression de port de travail (32), et le premier trou d'acquisition de pression de port de travail (21) est en communication avec le premier port de retour (R), de façon à ce que la cavité de détection de pression de port de travail (32) soit en communication avec le premier port de retour (R) à travers le premier trou de retour de pression de port de travail (26), la première cavité interne de bobine de soupape principale (2C1) et le premier trou d'acquisition de pression de port de travail (21) ;
    dans l'état où la bobine de soupape principale (2) est dans la seconde position de bobine de soupape principale, le premier trou de retour de pression de port de travail (26) est fermé par le corps de carter de soupape (1B) de façon à ce que le premier trou de retour de pression de port de travail (26) soit déconnecté de la cavité de détection de pression de port de travail (32), et la première cavité interne de bobine de soupape principale (2C1) est en communication avec le premier port de retour (R) à travers le premier trou d'acquisition de pression de port de travail (21).
  9. Soupape selon la revendication 5, dans laquelle :
    le second passage de retour comprend un second trou d'acquisition de pression de port de travail (8) qui passe à travers la paroi de bobine de soupape principale (2W) de la bobine de soupape principale (2) dans une direction croisant la direction axiale et qui ouvre vers la cavité de ressort de soupape de contrebalance (20), il y a un espace entre la bobine de soupape de contrebalance (3) et une paroi intérieure de la cavité de ressort de soupape de contrebalance (20) de la bobine de soupape principale (2), et lorsque la bobine de soupape de contrebalance (3) est dans chacune de la première position de soupape de contrebalance et seconde position de soupape de contrebalance, la cavité de ressort de soupape de contrebalance (20) est en communication avec le second trou d'acquisition de pression de port de travail (8) à travers l'espace.
  10. Soupape selon la revendication 9, dans laquelle :
    un creux de siège de ressort de soupape de contrebalance (25) est formé sur une surface d'extrémité de l'extrémité du siège de ressort de soupape de contrebalance (4) sur une périphérie extérieure de l'extrémité du siège de ressort de soupape de contrebalance, et le creux de siège de ressort de soupape de contrebalance (25) et en communication avec l'espace pour constituer une partie de la cavité de ressort de soupape de contrebalance (20) .
  11. Soupape selon la revendication 9 ou 10, dans laquelle :
    le second passage de retour comprend en outre un second trou de retour de pression de port de travail (27) qui passe à travers la paroi de bobine de soupape principale (2W) de la seconde bobine principale (2) dans une direction croisant la direction axiale,
    le second passage de retour comprend en outre : un trou de communication de bobine de soupape de contrebalance (15C) formé dans le corps de bobine de soupape de contrebalance (3) est dans une direction croisant la direction axiale, et un trou axial de bobine de soupape de contrebalance (15) qui est formé dans le corps de bobine de soupape de contrebalance (3B) essentiellement dans la direction axiale et qui est en communication avec le trou de communication de bobine de soupape de contrebalance (15C) ;
    le second passage de retour comprend en outre une rainure de siège de ressort de soupape de contrebalance (16) formée à une surface d'extrémité de l'extrémité du siège de ressort de soupape de contrebalance (4) et s'étendant dans une direction croisant la direction axiale, la rainure de siège de ressort de soupape de contrebalance (16) est en communication avec à la fois le trou axial de bobine de soupape de contrebalance (15) et la cavité de ressort de soupape de contrebalance (20).
  12. Soupape selon la revendication 11, dans laquelle :
    dans l'état où la bobine de soupape principale (2) dans l'alésage de soupape principal (16) est dans la position médiane de bobine de soupape principale, la bobine de soupape de contrebalance (3) est dans la première position de bobine de soupape de contrebalance, le second trou de retour de pression de port de travail (27) est en communication avec à la fois la cavité de détection de pression de port de travail (32) et le trou de communication de bobine de soupape de contrebalance (15C), et le second trou d'acquisition de pression de port de travail (8) est en communication avec le second port de retour (36) de façon à ce que la cavité de détection de pression de port de travail (32) soit en communication avec le second port de retour (36) à travers le second trou de retour de pression de port de travail (27), le trou de communication de bobine de soupape de contrebalance (15C), le trou axial de bobine de soupape de contrebalance (15), la rainure de siège de ressort de soupape de contrebalance (16), la cavité de ressort de soupape de contrebalance (20) et le second trou d'acquisition de pression de port de travail (8),
    de préférence, la bobine de soupape de contrebalance (3) comprend en outre : un second creux de bobine de soupape de contrebalance (22) formé sur la périphérie extérieure du corps de bobine de soupape de contrebalance (3B), le trou de communication de bobine de soupape de contrebalance (15C) fait communiquer le second creux de bobine de soupape de contrebalance (22) avec le trou axial de bobine de soupape de contrebalance (15), et dans l'état où la bobine de soupape principale dans l'alésage de soupape principal est dans la position médiane de soupape principale, le second trou de retour de pression de port de travail (27) est en communication avec le trou de communication de bobine de soupape de contrebalance (15C) à travers le second creux de bobine de soupape de contrebalance (22).
  13. Soupape selon la revendication 11, dans laquelle :
    dans l'état où la bobine de soupape principale (2) dans l'alésage de soupape principal (1C) est dans la première position de bobine de soupape principale, la bobine de soupape de contrebalance (3) est dans la seconde position de bobine de soupape de contrebalance de façon à ce que la seconde extrémité (3E2) de la bobine de soupape de contrebalance (3) pénètre la cavité de ressort de soupape de contrebalance (20), la cavité de ressort de soupape de contrebalance (20) est en communication avec le second port de retour (36) à travers un espace entre le siège de ressort de soupape de contrebalance (4) et la paroi intérieure de la cavité de ressort de soupape de contrebalance (22) de la bobine de soupape principale (2), l'espace entre la bobine de soupape de contrebalance (3) et la paroi intérieure de la cavité de ressort de soupape de contrebalance (20) de la bobine de soupape principale (2), et le second trou d'acquisition de pression de port de travail (8) ; et
    dans l'état où la bobine de soupape principale (2) dans l'alésage de soupape principal (1C) est dans la première position de bobine de soupape principale, le second trou de retour de pression de port de travail (27) est fermé par le corps de carter de soupape (1B) de façon à ce que le second trou de retour de pression de port de travail (27) soit déconnecté de la cavité de détection de pression de port de travail (32).
  14. Soupape selon la revendication 11, dans laquelle :
    dans l'état où la bobine de soupape principale (2) dans l'alésage de soupape principal (1C) est dans la seconde position de bobine de soupape principale, le second trou de retour de pression de port de travail (27) est en communication avec à la fois la cavité de détection de pression de port de travail (32) et le trou de communication de bobine de soupape de contrebalance (15C), et le second trou d'acquisition de pression de port de travail (8) est en communication avec le second port de travail (34), de façon à ce que la cavité de détection de pression de port de travail (32) soit en communication avec le second port de travail (34) à travers le second trou de retour de pression de port de travail (27), le trou de communication de bobine de soupape de contrebalance (15C), le trou axial de bobine de soupape de contrebalance (15), la rainure de siège de ressort de soupape de contrebalance (16), la cavité de ressort de soupape de contrebalance (20) et le second trou d'acquisition de pression de port de travail (8),
    de préférence, la bobine de soupape de contrebalance (3) comprend en outre : un second creux de bobine de soupape de contrebalance (22) formé sur la périphérie extérieure du corps de bobine de soupape de contrebalance (3B), le trou de communication de bobine de soupape de contrebalance (15C) fait communiquer le second creux de bobine de soupape de contrebalance (22) avec le trou axial de bobine de soupape de contrebalance (15), et dans l'état où la bobine de soupape principale (2) dans l'alésage de soupape principal (1C) est dans la seconde position de soupape principale, le second trou de retour de pression de port de travail (27) est en communication avec le trou de communication de bobine de soupape de contrebalance (15C) à travers le creux de bobine de soupape de contrebalance (22).
  15. Système hydraulique (200) comprenant :
    la soupape (10) de la revendication 1.
EP19166519.9A 2018-04-13 2019-04-01 Soupape et système hydraulique équipé de celle-ci Active EP3553324B1 (fr)

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CN201810335255.1A CN110374949B (zh) 2018-04-13 2018-04-13 阀和具有该阀的液压系统

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CN112797207B (zh) * 2021-03-01 2022-09-06 四川长仪油气集输设备股份有限公司 先导式管道爆炸正反作用轴流式自闭阀

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DE2649775A1 (de) * 1976-10-29 1978-05-03 Linde Ag Ventil mit einem laengsschieber
DE3014202A1 (de) * 1980-04-14 1981-10-15 Linde Ag, 6200 Wiesbaden Schieberventil
US5878647A (en) * 1997-08-11 1999-03-09 Husco International Inc. Pilot solenoid control valve and hydraulic control system using same
DE19957952A1 (de) * 1999-12-02 2001-06-07 Mannesmann Rexroth Ag Hydraulisches Wegeventil zur lastunabhängigen Steuerung eines hydraulischen Verbrauchers von insbesondere einer mobilen Arbeitsmaschine
CN1170067C (zh) * 2001-12-07 2004-10-06 卢永松 液压平衡阀
DE102006006228A1 (de) * 2006-02-09 2007-08-16 Robert Bosch Gmbh Hydraulische Steueranordnung
CN100441885C (zh) * 2006-10-10 2008-12-10 太原理工大学 自动适应负载变化的液压平衡阀

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US20190316693A1 (en) 2019-10-17
DK3553324T3 (da) 2021-12-13
EP3553324A1 (fr) 2019-10-16
CN110374949B (zh) 2020-12-04

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